EP1816416B1 - Climatiseur - Google Patents

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Publication number
EP1816416B1
EP1816416B1 EP05805432.1A EP05805432A EP1816416B1 EP 1816416 B1 EP1816416 B1 EP 1816416B1 EP 05805432 A EP05805432 A EP 05805432A EP 1816416 B1 EP1816416 B1 EP 1816416B1
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EP
European Patent Office
Prior art keywords
refrigerant
heat exchanger
connection
connection end
indoor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP05805432.1A
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German (de)
English (en)
Other versions
EP1816416A4 (fr
EP1816416A1 (fr
Inventor
Shinichi c/o MITSUBISHI DENKI KABUSHIKI WAKAMOTO
Tomohiko c/o MITSUBISHI DENKI KABUSHIKI KASAI
Jiro c/oMITSUBISHI DENKI KABUSHIKI KAISHa OKAJIMA
Toshiyuki c/o MITSUBISHI DENKI KABUSHIKI NAKAMURA
Kunio c/o MITSUBISHI DENKI KABUSHIKI KAISHA TOJO
Takashi c/o MITSUBISHI DENKI KABUSHIKI OKAZAKI
Toshihiko c/o MITSUBISHI DENKI KABUSHIKI ENOMOTO
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication date
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Publication of EP1816416A1 publication Critical patent/EP1816416A1/fr
Publication of EP1816416A4 publication Critical patent/EP1816416A4/fr
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Publication of EP1816416B1 publication Critical patent/EP1816416B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/006—Compression machines, plants or systems with reversible cycle not otherwise provided for two pipes connecting the outdoor side to the indoor side with multiple indoor units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0231—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units with simultaneous cooling and heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/023—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units
    • F25B2313/0233—Compression machines, plants or systems with reversible cycle not otherwise provided for using multiple indoor units in parallel arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/0272—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using bridge circuits of one-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
    • F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators

Definitions

  • the present invention generally relates to an air conditioner applying a refrigeration cycle.
  • the present invention relates to a multi-split type air conditioner including an outdoor unit and a plurality of indoor units, performing in operation modes where all of the rooms are cooled and heated, and in other operation modes where one of the rooms is cooled while another one of the rooms is heated, simultaneously.
  • Patent Document 1 discloses a multi-split type air conditioner, which includes an outdoor unit having a compressor and an outdoor heat exchanger, a plurality of indoor units, each having an indoor heat exchanger, and a relay device for connection between the outdoor unit and the indoor units.
  • the multi-split type air conditioner performs in the cooling and heating operation modes cooling and heating all of the rooms, respectively. Also, it performs in other operation modes cooling one of the rooms while heating another one of the rooms simultaneously, which are referred to as a principally-cooling operation mode where cooling operation capacity is greater than heating operation capacity, and as a principally-heating operation mode where heating operation capacity is greater than cooling operation capacity.
  • the conventional air conditioner requires a vapor-liquid separation device for separating vapor refrigerant and liquid refrigerant from the refrigerant in a vapor-liquid mixed state generated by the outdoor heat exchanger of the outdoor unit.
  • a first bypass pipe has one end connected to a liquid-phase outlet of the vapor-liquid separation device and a plurality of other split ends, each of which connects to a flow control device of the indoor unit.
  • the flow control device of the indoor unit in the room to be cooled depressurizes the high-pressurized liquid refrigerant for changing to the two-phase vapor-liquid refrigerant of low temperature and low pressure, which is supplied to the indoor heat exchanger.
  • the vapor refrigerant output from the vapor-liquid separation device is supplied to the indoor unit of the room to be heated.
  • Patent Document 1 JP 9-042804, A
  • the liquid refrigerant output from the vapor-liquid separation device is saturated liquid, unless it is overcooled, it may somehow be depressurized in a way up to the flow control device of the indoor unit so as to change its phase to the two-phase vapor-liquid phase, thereby causing noise and pressure pulsation in the flow control device.
  • a second bypass pipe is arranged adjacent and connected to the first bypass pipe, and another flow control device for controlling the flow through the second bypass pipe, which depressurizes a portion of the liquid refrigerant output from the vapor-liquid separation device to generate the two-phase vapor-liquid refrigerant of low temperature and low pressure, thereby overcooling the liquid refrigerant output from the vapor-liquid separation device with the vapor-liquid refrigerant through the second bypass pipe.
  • another flow control device intervenes in the first bypass pipe for controlling flow amount of the liquid refrigerant output from the vapor-liquid separation device for preventing the liquid refrigerant from being mixed in the vapor refrigerant.
  • one of the aspects of the present invention is to provide a multi-split type air conditioner using the refrigerant of carbon dioxide, which substantially reduces the number of components of the relay device and improves controllability of the cooling and heating features of the indoor heat exchangers.
  • an air conditioner of one of the aspects according to the present invention is to provide an air conditioner including an outdoor unit, a plurality of indoor units, and a relay device for connection between the outdoor unit and each of the indoor units.
  • the outdoor unit includes an outdoor heat exchanger, a compressor for pressurizing a refrigerant of carbon dioxide or a composite having main ingredient of carbon dioxide, and a first switching member for switching a flow direction of the refrigerant through the outdoor heat exchanger, which are in fluid communication between first and second connection ends.
  • Each of the indoor units includes an indoor heat exchanger and a first flow controller which are in fluid communication between first and second pipe connection ports.
  • the relay device includes a plurality of second switching members, each of which the second switching members selectively connects the first pipe connection port of the respective indoor unit with the first or second connection end of the outdoor unit.
  • the relay device also includes a first bypass pipe for connection between the second connection end of the outdoor unit and each of the second pipe connection ports of the indoor units, and a second flow controller intervening in the first bypass pipe.
  • the refrigerant flows through the refrigerant delivery port of the compressor, the first switching member, the outdoor heat exchanger, and the second connection end into the indoor unit in the room to be heated, in which the refrigerant heats the air in the indoor heat exchanger.
  • the refrigerant flows into the indoor units in the rooms to be cooled, in which after the refrigerant is depressurized when passing through the first flow controller for cooling the air in the indoor heat exchangers of the indoor units, following to the first connection end.
  • the refrigerant of carbon dioxide or a composite having main ingredient of carbon dioxide remains in a supercritical state while flowing from the refrigerant delivery port of the compressor prior to the indoor heat exchangers of the indoor units.
  • the noise and the pressure pulsation which might be generated at the first flow controller can be suppressed or avoided.
  • the vapor-liquid separation device 40 and associated components can be eliminated, which substantially reduce the number of the components of the relay device. Also, the controllability of the indoor heat exchanger for heating and cooling the rooms can fairly be improved due to the fewer components.
  • Fig. 1 illustrates the first example of an air conditioner not part of the present invention.
  • the air conditioner 2 uses carbon dioxide as a refrigerant, and includes, in general, an outdoor unit 4, a plurality of indoor units 6, and a relay device 8 for connection between the outdoor unit 4 and the indoor units 6. While there are shown three of the indoor units 6 (i.e., 6P, 6Q, 6R) in the present example, the present example cannot be limited by the number of the indoor units 6, as long as the air conditioner has more than two of the indoor units.
  • the air conditioner 2 performs in a cooling operation mode in which each of the rooms having the respective indoor unit is to be cooled, and in a heating operation mode in which each of the rooms is to be heated. Also, it performs in another two modes where one of the rooms is cooled while another one of the rooms is heated, simultaneously (i.e., principally-cooling and principally-heating operation modes).
  • the indoor unit 4 includes a compressor 10 for compressing the refrigerant, a heat exchanger (outdoor heat exchanger) 12, and a first switching member 16 such as a four-way switching valve, all of which are in fluid communication between first and second connection end 20a, 20b.
  • the compressor 10 has a refrigerant delivery port 10a and a refrigerant suction port 10b connected to the first switching member 16 via the pipes 14a, 14b, respectively.
  • the first switching member 16 is also connected via the pipe 14d to the first connection end 20a which is in turn connected to a pipe 18a of the relay device 8.
  • the heat exchanger 12 has one end 12a connected to the first switching member 16 via the pipe 14c and the other end connected via the pipe 14e to a second connection end 20b which is in turn connected to another pipe 18b of the relay device 8.
  • the pipes 18a, 18b are referred to as inter-unit pipes for connection between the outdoor unit 4 and the indoor units 6P-6R.
  • the switching member 16 is designed to switch a flow direction of the refrigerator through the heat exchanger 12 between first and second flow conditions in accordance with the operation modes.
  • the first connection end 20a is connected to the refrigerant suction port 10b of the compressor 10 via the pipes 14d, 14b
  • the refrigerant delivery port 10a of the compressor 10 is connected to one end 12a of the heat exchanger 12 via the pipes 14a, 14c, in which the refrigerant flows from one end 12a to the other end 12b of the heat exchanger 12, i.e., from the first connection end 20a to the second connection end 20b.
  • the second flow condition as illustrated in Fig.
  • one end 12a of the heat exchanger 12 is connected to the refrigerant suction port 10b of the compressor 10 via the pipes 14c, 14b, and the refrigerant delivery port 10a of the compressor 10 is connected to the first connection end 20a via the pipes 14a, 14d, in which the refrigerant flows from the other end 12b to one end 12a of the heat exchanger 12, i.e., from the second connection end 20b to the first connection end 20a.
  • a relay device 8 includes a plurality of three-way switching valves (second switching member) 22, e.g., three of the switching valves 22P, 22Q, 22R in the present example, each of which has three of connection ports 24a, 24b, 24c.
  • One inter-unit pipe 18a is split and connected to the connection ports 24a of the switching valves 22P, 22Q, 22R, and the other inter-unit pipe 18b is also split and connected to the connection ports 24b of the switching valves 22P, 22Q, 22R.
  • each of the connection ports 24c of the switching valves 22P, 22Q, 22R is connected to the first pipe connection port 26a of the respective indoor unit 6.
  • Each of the indoor units 6 includes another heat exchanger (indoor heat exchanger) 28 and a flow control valve (first flow controller) 32, which are in fluid communication between first and second pipe connection ports 26a, 26b.
  • the heat exchanger 28 has one end connected via a pipe to the first pipe connection port 26a, and the other end connected via a pipe 30 to the second pipe connection port 26b which is in turn connected to a bypass pipe of the relay member 8.
  • the flow control valves 32 (32P, 32Q, 32R) intervene in the pipe 30 for controlling the flow of the refrigerant therethrough.
  • the relay device includes the first bypass pipe 30 having one end connected to the inter-unit pipe 18b and the other end split and connected to each of the second pipe connection ports 26b (and the flow control valves 32). Also, a second flow control valve 36 intervenes in the bypass pipe 30 for controlling the flow of refrigerant through the bypass pipe 30.
  • FIGs. 2-5 illustrating the flow of the refrigerant
  • Figs. 6-9 of the p-h diagram showing the relationship between the pressure and the enthalpy of the refrigerant.
  • the switching member 16 switches to the first flow condition (by connecting the refrigerant delivery port 10a of the compressor 10 with one end 12a of the heat exchanger 12 and by connecting the refrigerant suction port 10b with the first connection end 20a), the second flow control valve 36 is fully opened, and the first flow control valves 32P-32R is throttled. Also, the connection port 24b of the three-way switching valve 22 is closed while the connection ports 24a, 24c are opened. In this arrangement, the compressor 10 initiates to be driven.
  • Pressurization by the compressor 10 changes the vapor refrigerant of low pressure and low temperature to one of high pressure and high temperature, which is delivered from the refrigerant delivery port 10a.
  • the refrigerant is pressurized adiabatically, i.e., without heat exchange with ambient air, which is described by a constant-enthalpy line [1]-[2] in the p-h diagram (pressure-enthalpy diagram) of Fig. 6 .
  • the refrigerant of high pressure and high temperature flows through the first switching member 16 and heats the ambient air in the heat exchanger 12 to lower the temperature of the refrigerant.
  • the pressure thereof is kept almost constant but slightly declining due to pressure loss in the heat exchanger 12 as the refrigerant is cooled, which is represented by a almost flat line [2]-[3] in the p-h diagram.
  • the refrigerant of carbon dioxide according to the present invention is kept in a supercritical state at high temperature and lowers the temperature without condensation.
  • the refrigerant from the heat exchanger 12 flows through the second connection end 20b and the bypass pipe 34, while the flow control valve 36 is fully opened, into each of the indoor units 6P-6R, in which throttling the flow control valves 32P-32R changes (depressurizes) the refrigerant to the two-phase vapor-liquid refrigerant of low temperature and low pressure.
  • the refrigerant is depressurized at the flow control valves 32P-32R under the constant enthalpy, which is represented by a vertical line [3]-[4] of the p-h diagram.
  • the two-phase vapor-liquid refrigerant of low temperature and low pressure As the two-phase vapor-liquid refrigerant of low temperature and low pressure is changing to the vapor refrigerant of low temperature and low pressure, it refrigerates (absorbs heat from) the ambient air in the heat exchanger 28.
  • the pressure of the refrigerant is kept almost constant but slightly declining due to pressure loss in the heat exchanger 28 as the refrigerant absorbs heat, which is represented by a almost flat line [4]-[1] in the p-h diagram.
  • the vapor refrigerant of low temperature and low pressure from the heat exchanger 28 returns through the three-way switching valves 22, the first connection end 20a, and the first switching member 16, into the compressor 10.
  • the switching member 16 switches to the second flow condition (by connecting the refrigerant delivery port 10a of the compressor 10 with the first connection end 20a and by connecting the refrigerant suction port 10b with one end 12a of the heat exchanger 12), the second flow control valve 36 is fully opened, and the first flow control valves 32P-32R is throttled. Also, the connection port 24b of the three-way switching valve 22 is closed while the connection ports 24a, 24c are opened. In this arrangement, the compressor 10 initiates to be driven.
  • Pressurization by the compressor 10 changes the vapor refrigerant of low pressure and low temperature (point [1]) to one of high pressure and high temperature, which is delivered from the refrigerant delivery port 10a.
  • the refrigerant of high pressure and high temperature (point [2]) flows through the first switching member 16, the first connection end 20a, and the three-way switching valves 22 into each one of the heat exchangers 28 of the indoor units 6P-6R.
  • the refrigerant heats the ambient air in the heat exchangers 28 thereby to lower the temperature of the refrigerant (point [3]), and is depressurized by the flow control valve 32 to be changed as the two-phase vapor-liquid refrigerant of low temperature and low pressure (point [4]).
  • the refrigerant from each of the indoor units 6P-6R flows through the bypass pipe 34 and the second connection end 20b to the other end 12b of the heat exchanger 12.
  • the two-phase vapor-liquid refrigerant refrigerates (absorbs heat from) the ambient air in the heat exchanger 12 to be the vapor refrigerant of low temperature and low pressure (point [1]), which returns to the compressor 10 through the switching member 16.
  • the switching member 16 switches to the first flow condition (by connecting the refrigerant delivery port 10a of the compressor 10 with one end 12a of the heat exchanger 12 and by connecting the refrigerant suction port 10b with the first connection end 20a). Also, the second flow control valve 36 is closed, and the first flow control valves 32P and 32Q are throttled, while the valve 32R is fully opened. Further, each of the three-way switching valves 22P and 22Q has the connection port 24b being closed and the connection ports 24a and 24c being opened. The three-way switching valve 22R has the connection port 24a being closed and the connection ports 24b and 24c being opened. In this arrangement, the compressor 10 initiates to be driven.
  • Pressurization by the compressor 10 changes the vapor refrigerant of low pressure and low temperature (point [1]) to one of high pressure and high temperature, which is delivered from the refrigerant delivery port 10a.
  • the refrigerant of high pressure and high temperature (point [2]) flows through the first switching member 16 to the heat exchanger 12, heating the ambient air in the heat exchanger 12 thereby to lower the temperature of the refrigerant (point [3]).
  • the refrigerant of high pressure from the heat exchanger 12 flows through the second connection end 20b and the three-way switching valve 22R into the indoor unit 6R to heat the ambient air in the heat exchanger 28 to lower the temperature of the refrigerant (point [4]). Then, the refrigerant is depressurized by the flow control valve 32P and 32Q to be the two-phase vapor-liquid refrigerant of low temperature and low pressure (point [5]). The refrigerant refrigerates (absorbs heat from) the ambient air in the heat exchanger 28 of the indoor units 6P, 6Q, changing to the vapor refrigerant of low temperature and low pressure (point [1]).
  • the refrigerant from the indoor units 6P, 6Q passes through the three-way switching valve 22P and 22Q, the first connection end 20a, and the switching member 16, and returns to the compressor 10.
  • the refrigerant of carbon dioxide according to the present invention can be kept in a supercritical state while flowing from the refrigerant delivery port 10a of the compressor 10 through the first switching member 16, the indoor heat exchanger 12, the indoor unit 6R, and the flow control valves 32P and 32Q of the indoor units 6P and 6Q. Therefore, noise and pressure pulsation can be avoided or reduced, which might otherwise be generated at the flow control valves 32P and 32Q of the indoor units 6P and 6Q.
  • the air conditioner 2' includes the vapor-liquid separation device intervening in the inter-unit pipe 18b within the relay device 8', and the bypass pipe 34 is connected to the liquid-phase port of the vapor-liquid separation device 40.
  • the switching member 16 switches to the first flow condition (by connecting the refrigerant delivery port 10a of the compressor 10 with one end 12a of the heat exchanger 12 and by connecting the refrigerant suction port 10b with the first connection end 20a). Also, the second flow control valve 36 and the first flow control valves 32P, 32Q are throttled, while the valve 32R is fully opened. Further, each of the three-way switching valves 22P, 22Q has the connection port 24b being closed and the connection ports 24a, 24c being opened. The three-way switching valve 22R has the connection port 24a being closed and the connection ports 24b and 24c being opened. In this arrangement, the compressor 10 initiates to be driven.
  • Pressurization by the compressor 10 changes the fluorocarbon-based vapor refrigerant of low pressure and low temperature (point [1]) to one of high pressure and high temperature, which is delivered from the refrigerant delivery port 10a.
  • the refrigerant of high pressure and high temperature flows through the first switching member 16 to the heat exchanger 12, in which the refrigerant heats the ambient air in the heat exchanger 12 to partially condense thereby to be the two-phase vapor-liquid refrigerant of high pressure, since the pressure of the refrigerant coming into the heat exchanger 12 is lower than the critical pressure.
  • the two-phase vapor-liquid refrigerant from the heat exchanger 12 enters the vapor-liquid separation device 40.
  • the vapor refrigerant runs through the three-way valve 22R into the heat exchanger 28 of the indoor unit 6R, in which the vapor refrigerant heats the ambient air in the heat exchanger 28 to condense, thereby changing to the liquid refrigerant of high pressure that passes through the flow control valve 32R.
  • another liquid refrigerant in the vapor-liquid separation device 40 flows through the flow control valve 36 and joins with the former liquid refrigerant from the indoor unit 6R, both of which liquid refrigerant come into the indoor units 6P, 6Q. Then, the refrigerant is depressurized by the flow control valve 32P, 32Q, changing to the two-phase vapor-liquid refrigerant of low temperature and low pressure.
  • the refrigerant refrigerates (absorbs heat from) the ambient air in the heat exchanger 28, further changing to the vapor refrigerant of low temperature and low pressure.
  • the refrigerant from the indoor units 6P, 6Q passes through the three-way switching valve 22P, 22Q and the switching member 16, and returns to the compressor 10.
  • the flow control valve 36 controls the flow amount of the liquid refrigerant running from the vapor-liquid separation device 40 so that the vapor refrigerant running from the vapor-liquid separation device 40 into the indoor unit 6R contains no liquid refrigerant.
  • the liquid refrigerant is depressurized when passing through the flow control valve 36 and the bypass pipe 34.
  • the liquid refrigerant running from the vapor-liquid separation device 40 is the saturated refrigerant, it can be the two-phase vapor-liquid refrigerant by depressurization, which causes noise and pressure pulsation generated when the vapor-liquid refrigerant passes the flow control valves 33P, 33Q of the indoor units 6P, 6Q.
  • the conventional air conditioner 2' requires a feature designed for overcooling the liquid refrigerant running from the vapor-liquid separation device 40.
  • a second bypass pipe 42 is arranged adjacent the first bypass pipe 34, which has one end connected to a portion of the first bypass pipe 34 downstream of the flow control valve 36 and the other end connected to the inter-unit pipe 18a.
  • another flow control valve 44 is provided intervening in the second bypass pipe 42. This allows the liquid refrigerant at the flow control valve 44 to expand (depressurize) by throttling the flow control valve 44 thereby to obtain the two-phase vapor-liquid refrigerant of low temperature and low pressure.
  • the second bypass pipe 42 with the vapor-liquid refrigerant overcools the refrigerant through the first bypass pipe 34 in regions between the vapor-liquid separation device 40 and the flow control valve 36 and between the flow control valve 36 and the connection portion.
  • the flow control valve 36 may be adjusted so that a portion of the refrigerant passes through the first bypass pipe 34, bypassing the indoor unit 6R. This prevents increase of the refrigerant flow, which may cause the refrigerant noise and the corrosion of the pipe.
  • the switching member 16 switches to the second flow condition (by connecting the refrigerant delivery port 10a of the compressor 10 with the first connection end 20a and by connecting the refrigerant suction port 10b with one end 12a of the heat exchanger 12). Also, the second flow control valve 36 is throttled, and the first flow control valves 32P, 32Q are fully opened, while the first flow control valve 32R is throttled. Further, each of the three-way switching valves 22P, 22Q has the connection port 24b being closed and the connection ports 24a, 24c being opened. The three-way switching valve 22R has the connection port 24a being closed and the connection ports 24b and 24c being opened. In this arrangement, the compressor 10 initiates to be driven.
  • Pressurization by the compressor 10 changes the vapor refrigerant of low pressure and low temperature (point [1]) to one of high pressure and high temperature, which is delivered from the refrigerant delivery port 10a.
  • the refrigerant of high pressure and high temperature (point [2]) flows through the first switching member 16 and the three-way switching valve 22P, 22Q to the heat exchangers 28 of the indoor units 6P, 6Q, heating the ambient air in the heat exchangers 28 thereby to lower the temperature of the refrigerant (point [3]).
  • the refrigerant entering the indoor unit 6R expands (depressurizes) at the flow control valve 32R, changing to the two-phase vapor-liquid refrigerant of low temperature and low pressure (point [4]). Also, the refrigerant all or partially evaporates to refrigerate the ambient air in the heat exchanger 28 (point [5]) and enters the three-way switching valves 22R.
  • the refrigerant passing out of the heat exchanger 28 (point [5]) is the two-phase vapor-liquid refrigerant having the dryness close to 1.0.
  • the remaining portion of the refrigerant (point [3]) bypasses the indoor unit 6R through the bypass pipe 34 and expands (depressurizes) at the flow control valve 36, changing to the two-phase vapor-liquid refrigerant of low temperature and low pressure (point [6]).
  • the refrigerant passing out of the flow control valve 36 (point [6]) has the pressure slightly less than that of the refrigerant passing out of the heat exchanger 28 (point [5]).
  • the air conditioner according to the present example controls the refrigerant flow passing through the indoor unit that performs the cooling operation with adjustment of the flow control valve 36, thereby improving the operation efficiency.
  • Fig. 11 illustrates the embodiment of an air conditioner according to the present invention.
  • the outdoor unit 4A of the air conditioner 2A includes a flow-path selecting member 52 in addition to the structure of the air conditioner 2 of the first example.
  • the flow-path selecting member 52 is designed such that the refrigerant flows from the outdoor unit 4A into the relay device 8A always through the second connection end 20b, and from the relay device 8A to the outdoor unit 4A always through the first connection end 20a, regardless of the operation modes.
  • the flow-path selecting member 52 includes a pair of check valves 54, 56, intervening in the pipes between the first switching member 16 and the first connection end 20a, and between the heat exchanger 12 and the second connection end 20b, respectively.
  • the check valve 54 allows the refrigerant to flow only in a direction from the first connection end 20a to the switching member 16, and the check valve 56 allows the refrigerant to flow only in a direction from the heat exchanger 12 to the second connection end 20b.
  • the flow-path selecting member 52 includes a bypass pipe 58 having one end connected to an intermediate point of the pipe 14d between the switching member 16 and check valve 54 and the other end connected to the second connection end 20b.
  • a check valve 60 is provided intervening in the bypass pipe 58, which allows the refrigerant to flow only in a direction from the switching member 16 to the second connection end 20b.
  • the flow-path selecting member 52 includes a bypass pipe 62 having one end connected to the first connection end 20a and the other end connected to an intermediate point of the pipe 14e between the heat exchanger 12 and the check valves 56.
  • a check valve 60 is provided intervening in the bypass pipe 62, which allows the refrigerant to flow only in a direction from the first connection end 20a to the heat exchanger 12.
  • the relay device 8A includes a second bypass pipe 66 connecting between the first bypass pipe 34 and the inter-unit pipe 18a, and a third flow control valve 68 intervening in the second bypass pipe 66 for controlling the refrigerant flow running therethrough.
  • the switching member 16 switches to the first flow condition (by connecting the refrigerant delivery port 10a of the compressor 10 with one end 12a of the heat exchanger 12 and by connecting the refrigerant suction port 10b with the first connection end 20a), the second flow control valve 36 is fully opened, and the first flow control valves 32P-32R is throttled, while the third flow control valve 68 is closed. Also, the connection ports 24b of the three-way switching valves 22 are closed while the connection ports 24a, 24c are opened. In this arrangement, the compressor 10 initiates to be driven.
  • Pressurization by the compressor 10 changes the vapor refrigerant of low pressure and low temperature to one of high pressure and high temperature, which is delivered from the refrigerant delivery port 10a.
  • the refrigerant of high pressure and high temperature flows through the first switching member 16 into the heat exchanger 12, heating the ambient air in the heat exchanger 12 thereby to lower the temperature of the refrigerant without condensation.
  • the refrigerant of high pressure from the heat exchanger 12 flows through the check valve 56, the second connection end 20b, and the first bypass pipe 34 (the second flow control valve 36 is fully opened) to the indoor units 6P-6R, in which the refrigerant expands (depressurizes) at the flow control valves 32P-32R, changing to the two-phase vapor-liquid refrigerant of low temperature and low pressure.
  • the refrigerant refrigerates (absorbs heat from) the ambient air in the heat exchanger 28, changing to the vapor refrigerant of low temperature and low pressure.
  • the refrigerant from the heat exchangers 28 of the indoor units 6P-6R flows through the three-way switching valve 22P-22R and the first connection end 20a.
  • the refrigerant at the first connection end 20a has pressure less than the refrigerant between the heat exchanger 12 and the check valve 64 so that it is automatically guided to pass through the check valve 54 and the first switching member 16 back to the compressor 10.
  • the switching member 16 switches to the second flow condition (by connecting the refrigerant delivery port 10a of the compressor 10 with the first connection end 20a and by connecting the refrigerant suction port 10b with one end 12a of the heat exchanger 12), the second flow control valve 36 is fully opened, and the first flow control valves 32P-32R is throttled while the third flow control valve 68 is fully opened. Also, the connection port 24a of the three-way switching valve 22 is closed while the connection ports 24b, 24c are opened. In this arrangement, the compressor 10 initiates to be driven.
  • Pressurization by the compressor 10 changes the vapor refrigerant of low pressure and low temperature to one of high pressure and high temperature, which is delivered from the refrigerant delivery port 10a.
  • the refrigerant of high pressure and high temperature flows through the first switching member 16, the check valve 60, the second connection end 20b, and the three-way switching valves 22 to each one of the heat exchangers 28 of the indoor units 6P-6R.
  • the refrigerant heats the ambient air in the heat exchangers 28 to lower the temperature of the refrigerant, and is depressurized by the flow control valve 32, changing to the two-phase vapor-liquid refrigerant of low temperature and low pressure.
  • the refrigerant from each of the indoor units 6P-6R flows through the first bypass pipe 34 and the third flow control valve 68 (the second bypass pipe 66) into the first connection end 20a.
  • the refrigerant at the first connection end 20a has pressure less than the refrigerant between the switching member 16 and the check valve 54 so that it is automatically guided through the check valve 64 to the other end 12b of the heat exchanger 12.
  • the two-phase vapor-liquid refrigerant refrigerates (absorbs heat from) the ambient air in the heat exchanger 12, changing to the vapor refrigerant of low temperature and low pressure, which runs through the switching member 16 back to the compressor 10.
  • the switching member 16 switches to the first flow condition (by connecting the refrigerant delivery port 10a of the compressor 10 with one end 12a of the heat exchanger 12 and by connecting the refrigerant suction port 10b with the first connection end 20a). Also, the second and third flow control valves 36, 68 are closed, and the first flow control valves 32P, 32Q are throttled, while the first flow control valve 32R is fully opened. Further, each of the three-way switching valves 22P, 22Q has the connection port 24b being closed and the connection ports 24a and 24c being opened. The three-way switching valve 22R has the connection port 24a being closed and the connection ports 24b, 24c being opened. In this arrangement, the compressor 10 initiates to be driven.
  • Pressurization by the compressor 10 changes the vapor refrigerant of low pressure and low temperature to one of high pressure and high temperature, which is delivered from the refrigerant delivery port 10a.
  • the refrigerant of high pressure and high temperature flows through the first switching member 16 into the heat exchanger 12, heating the ambient air in the heat exchanger 12 thereby to lower the temperature of the refrigerant.
  • the refrigerant of high pressure from the heat exchanger 12 flows through the check valve 56, the second connection end 20b, and the three-way switching valve 22R into the indoor unit 6R, heating the ambient air in the heat exchanger 28 thereby to lower the temperature of the refrigerant.
  • the refrigerant is depressurized by the flow control valve 32P, 32Q, changing to the two-phase vapor-liquid refrigerant of low temperature and low pressure.
  • the refrigerant refrigerates (absorbs heat from) the ambient air in the heat exchanger 28 of the indoor units 6P, 6Q, changing to the two-phase vapor-liquid refrigerant of low temperature and low pressure.
  • the refrigerant from the indoor units 6P, 6Q passes through the three-way switching valve 22P, 22Q into the first connection end 20a.
  • the refrigerant at the first connection end 20a has pressure less than the refrigerant between the heat exchanger 12 and the check valve 64 so that it is automatically guided to pass through the check valve 54 and the switching member 16 back to the compressor 10.
  • the flow control valve 36 may be adjusted so that a portion of the refrigerant passes through the first bypass pipe 34 bypassing the indoor unit 6R. This prevents increase of the refrigerant flow, which may cause the refrigerant noise and the corrosion of the pipe.
  • the switching member 16 switches to the second flow condition (by connecting the refrigerant delivery port 10a of the compressor 10 with the first connection end 20a and by connecting the refrigerant suction port 10b with one end 12a of the heat exchanger 12). Also, the second flow control valve 36 is closed, and the first flow control valves 32P, 32Q are fully opened, while the first flow control valve 32R and the third flow control valve 68 are throttled. Further, each of the three-way switching valves 22P, 22Q has the connection port 24a being closed and the connection ports 24b, 24c being opened. The three-way switching valve 22R has the connection port 24b being closed and the connection ports 24a, 24c being opened. In this arrangement, the compressor 10 initiates to be driven.
  • Pressurization by the compressor 10 changes the vapor refrigerant of low pressure and low temperature to one of high pressure and high temperature, which is delivered from the refrigerant delivery port 10a.
  • the refrigerant of high pressure and high temperature flows through the first switching member 16 and the three-way switching valve 22P, 22Q into the heat exchangers 28 of the indoor units 6P and 6Q, heating the ambient air in the heat exchangers 28 thereby to lower the temperature of the refrigerant.
  • the refrigerant entering the indoor unit 6R expands (depressurizes) at the flow control valve 32R, changing to the two-phase vapor-liquid refrigerant of low temperature and low pressure. Also, the refrigerant all or partially evaporates to refrigerate the ambient air in the heat exchanger 28 and enters the three-way switching valves 22R.
  • the remaining portion of the refrigerant bypassing the indoor unit 6R passes through the first and second bypass pipes 34, 66 and expands (depressurizes) at the flow control valve 68 to be two-phase vapor-liquid refrigerant of low temperature and low pressure.
  • the refrigerant passing out of the flow control valve 68 joins with the refrigerant passing out of the three-way control valve 22R to be the two-phase vapor-liquid refrigerant, which flows into the first connection end 20a of the outdoor unit 4.
  • the refrigerant at the first connection end 20a has pressure less than the refrigerant between the switching member 16 and the check valve 54 so that it is automatically guided to return through the check valve 64 to the other end 12a of the heat exchanger 12.
  • the two-phase vapor-liquid refrigerant refrigerates the ambient air in the heat exchanger 12 to change itself to be vapor refrigerant of low temperature and low pressure in the heat exchanger 12, which returns through the switching member 16 to the compressor 10.
  • the air conditioner of the present embodiment has another advantage in addition to those of the first example. That is, a pair of the inter-unit pipes connecting between the outdoor unit 4A and the indoor unit 6P-6R can be designed such that the refrigerant of high pressure flows only through one of the pipes 18b, and the refrigerant of low pressure flows only through the other one of the pipes 18a. Therefore, the inter-unit pipe 18a may have the pipe wall thickness less than that of the inter-unit pipe 18b.
  • the three-way switching valve is used in the embodiment.
  • a pair of two-way valves 22, 23 may be adapted as illustrated in Fig. 12 .
  • the two-way valve 22 has one end connected to the inter-unit pipe 18a and the second bypass pipe 66, and the other end connected to the indoor unit 28.
  • the another two-way valve 23 has one end connected to the inter-unit pipe 18b and the other end connected to the indoor unit 28.
  • the flow directions of the refrigerant running through the inter-unit pipes 18a, 18b (and the two-way valves 22, 23) can be kept the same regardless the operation modes.
  • the switching member may have any other structures rather than the three-way control valves 22P-22R, for selectively connecting the indoor heat exchanger 28 with the pipe 18a or 18b.
  • the flow-path selecting member 52 may have any other structures for allowing the refrigerant to flow from the outdoor unit 4A to the relay device 8A only through the connection end 20b and from the relay device 8A to the outdoor unit 4A only through the connection end 20a, in which the present invention is not limited to the structure shown in Fig. 11 .
  • the switching member 16 switches to the first flow condition by connecting the refrigerant delivery port 10a of the compressor 10 with one end 12a of the heat exchanger 12 and by connecting the refrigerant suction port 10b with the first connection end 20a
  • the flow-path selecting member 52 guides the refrigerant from the end 12b of the heat exchanger 12 to the connection end 20b and blocks it to the connection end 12a.
  • the switching member 16 switches to the second flow condition by connecting the refrigerant delivery port 10a of the compressor 10 with the first connection end 20a and by connecting the refrigerant suction port 10b with one end 12a of the heat exchanger 12
  • the flow-path selecting member 52 guides the refrigerant from the compressor 10 to the connection end 20b and blocks it to the connection end 12a. Any types of the flow-path selecting members having such structures are included in the present invention.
  • carbon dioxide itself is used as the refrigerant, however, any composites having main ingredient of carbon dioxide may be used as the refrigerant.
  • unit in the indoor and outdoor units is not intended to describe that all components are physically provided within or on the same housing.
  • the structure having the flow control valve of the indoor unit located at a position remote from the housing in which the indoor heat exchanger 28 is provided also falls within the scope of the present invention.
  • a plurality of pairs of outdoor heat exchangers and the compressors may be provided within the outdoor unit so that the refrigerant from each pairs of outdoor heat exchangers and the compressors join to flow from one of the inter-unit pipes, and the refrigerant from the other end of the inter-unit pipes is split to each pair of outdoor heat exchangers and the compressors.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
  • Air Conditioning Control Device (AREA)

Claims (1)

  1. Climatiseur (2), comprenant :
    une unité extérieure (4) incluant un échangeur de chaleur extérieur (12), un compresseur (10) pour mettre sous pression un réfrigérant à base de dioxyde de carbone ou d'un composite ayant comme ingrédient principal du dioxyde de carbone et un premier élément de commutation (16) pour commuter une direction d'écoulement du réfrigérant à travers l'échangeur de chaleur extérieur (12), qui sont en communication de fluide entre des première et deuxième extrémités de raccordement (20a, 20b) ;
    une pluralité d'unités intérieures (6), chacune desdites unités intérieures (6) incluant un échangeur de chaleur intérieur (28) et un premier régulateur de débit (32) qui sont en communication de fluide entre des premier et deuxième orifices de raccordement de tuyaux (26a, 26b) ; et
    un dispositif de relais (8) incluant une pluralité de deuxièmes éléments de commutation (22, 23), chacun des deuxièmes éléments de commutation (22, 23) raccordant sélectivement le premier orifice de raccordement de tuyau (26a) de l'unité intérieure respective (6) à l'une des première et deuxième extrémités de raccordement (20a, 20b) de l'unité extérieure (4), un premier tuyau de dérivation (34) pour le raccordement entre la deuxième extrémité de raccordement (20b) de l'unité extérieure (4) et chacun des deuxièmes orifices de raccordement de tuyau (26b) des unités intérieures (6), et un deuxième régulateur de débit (36) intervenant dans le premier tuyau de dérivation (34) ;
    dans lequel le compresseur (10) présente un orifice de distribution de réfrigérant (10a) et un orifice d'aspiration de réfrigérant (10b) et
    dans lequel le premier élément de commutation (16) commute en fonction des modes de fonctionnement du climatiseur (2) entre des première et deuxième conditions, la première condition permettant le raccordement de l'orifice de distribution de réfrigérant (10a) à une extrémité (12a) de l'échangeur de chaleur extérieur et le raccordement de l'orifice d'aspiration de réfrigérant (10b) à la première extrémité de raccordement (20a), la deuxième condition permettant le raccordement de l'orifice de distribution de réfrigérant (10a) à la deuxième extrémité de raccordement (20b) et le raccordement de l'orifice d'aspiration de réfrigérant (10b) à ladite première extrémité (12a) de l'échangeur de chaleur extérieur (12), et le climatiseur comprenant en outre :
    un sélecteur de chemin d'écoulement (52) pour guider le réfrigérant de l'échangeur de chaleur extérieur (12) vers la deuxième extrémité de raccordement (20b) et guider le réfrigérant de la première extrémité de raccordement (20a) vers l'orifice d'aspiration de réfrigérant (10b) lorsque le premier élément de commutation (16) commute sur la première condition, et pour guider le réfrigérant de l'orifice de distribution de réfrigérant (10a) vers la deuxième extrémité de raccordement (20b) et guider le réfrigérant de la première extrémité de raccordement (20a) vers l'échangeur de chaleur extérieur (12) lorsque le premier élément de commutation (16) commute sur la deuxième condition ;
    un deuxième tuyau de dérivation (66) pour la communication de fluide entre la première extrémité de raccordement (20a) de l'unité extérieure (4) et le premier tuyau de dérivation (34) ;
    un troisième régulateur de débit (68) intervenant dans le deuxième tuyau de dérivation (66) ;
    caractérisé par
    un tuyau inter-unités (18b) entre la deuxième extrémité de raccordement (20b) et les deuxièmes éléments de commutation (22, 23),
    les modes de fonctionnement du climatiseur incluant : un mode de fonctionnement principalement de refroidissement dans lequel le nombre d'unités intérieures (6) en mode de refroidissement est supérieur au nombre d'unités intérieures (6) en mode de chauffage tandis qu'au moins l'une de la pluralité d'unités intérieures (6) fonctionne en mode de chauffage et au moins l'une des autres unités intérieures (6) fonctionne en mode de refroidissement, et un mode de fonctionnement principalement de chauffage dans lequel le nombre d'unités intérieures (6) en mode de chauffage est supérieur au nombre d'unités intérieures (6) en mode de refroidissement,
    dans lequel, dans le mode de fonctionnement principalement de refroidissement, ledit premier élément de commutation (16) est commuté sur la première condition, le deuxième régulateur de débit (36) est fermé, le troisième régulateur de débit (68) est fermé et le réfrigérant dans un état supercritique, délivré par le compresseur (10), est amené via l'échangeur de chaleur extérieur (12) à une unité de chauffage intérieure (6) en restant dans un état supercritique, puis amené au premier régulateur de débit (32) d'une unité de refroidissement intérieure (6) en restant toujours dans un état supercritique, puis amené à l'échangeur de chaleur intérieur (28) après avoir été décompressé dans un état à deux phases gaz-liquide au premier régulateur de débit (32), et ensuite amené à la première extrémité de raccordement (20a) ; et
    dans le mode de fonctionnement principalement de chauffage, le premier élément de commutation (16) est commuté sur ladite deuxième condition, le deuxième régulateur de débit (36) est fermé, le troisième régulateur de débit (68) est étranglé et le réfrigérant dans un état supercritique, délivré par le compresseur (10), est amené à une unité de chauffage intérieure (6) par le tuyau inter-unités (18b) et des deuxièmes éléments de commutation (22, 23) en restant dans un état supercritique, puis amené au premier régulateur de débit (32) d'une unité de refroidissement intérieure (6) et une partie du réfrigérant s'écoule vers le troisième régulateur de débit (68) en restant toujours dans un état supercritique, et la partie restante du réfrigérant est décompressée au premier régulateur de débit (32) puis conduite à travers l'échangeur de chaleur intérieur (28) et fusionne avec le réfrigérant décompressé au troisième régulateur de débit (68) avant de s'écouler ensemble vers la première extrémité de raccordement (20a).
EP05805432.1A 2004-11-25 2005-11-01 Climatiseur Active EP1816416B1 (fr)

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JPWO2011048646A1 (ja) * 2009-10-19 2013-03-07 三菱電機株式会社 熱媒体変換機及び空気調和装置
WO2011048695A1 (fr) 2009-10-23 2011-04-28 三菱電機株式会社 Dispositif de conditionnement d'air
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CN101065623A (zh) 2007-10-31
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JP4752765B2 (ja) 2011-08-17
JPWO2006057141A1 (ja) 2008-06-05
US20090145151A1 (en) 2009-06-11
EP1816416A4 (fr) 2011-08-03
EP1816416A1 (fr) 2007-08-08

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